ATBECHDEDKESFRGBGRITLILUNLSEMCPTIE......FI......................................JDIM350 (Ver 2.1 Jan 2001) 2100000/00866299EUROPEAN PATENT SPECIFICATIONB120021211EP96925106.5199607261998022720010131jaenen1932049519950728JP200212112002501998092319983920021211200250200202257 7F 28D 9/00 A 7F 28F 3/08 BdeWÄRMETAUSCHERenHEAT EXCHANGERfrECHANGEUR DE CHALEUREP-A- 0 796 986WO-A-81/02060BE-A- 444 542DE-A- 2 408 462DE-A- 4 333 904GB-A- 320 279JP-B- 48 044 530JP-B- 51 033 293JP-T- 57 500 945US-A- 4 384 611US-A- 5 340 664PATENT ABSTRACTS OF JAPAN vol. 006, no. 061 (M-123), 20 April 1982 (1982-04-20) -& JP 57 002983 A (TOSHIBA CORP), 8 January 1982 (1982-01-08)1999110310ENDOU, Tsuneo Kabushiki Kaisha Honda GijutsuKenkyusho 4-1, Chuo 1-chome Wako-shiSaitama-ken 351-01JPTAKAHASHI, Tsutomu Kabushiki Kaisha HondaGijutsu Kenkyusho 4-1, Chuo 1-chome Wako-shiSaitama-ken 351-01JPYANAI, Hideyuki Kabushiki Kaisha Honda GijutsuKenkyusho 4-1, Chuo 1-chome Wako-shiSaitama-ken 351-01JPKAWAMURA, Toshiki Kabushiki Kaisha Honda GijutsuKenkyusho 4-1, Chuo 1-chome Wako-shiSaitama-ken 351-01JPWAKAYAMA, Tokiyuki Kabushiki Kaisha HondaGijutsu Kenkyusho 4-1, Chuo 1-chome Wako-shiSaitama-ken 351-01JPHONDA GIKEN KOGYO KABUSHIKI KAISHA0023783838.15.676881-1, Minami Aoyama 2-chomeMinato-ku, Tokyo 107JPLeale, Robin George00032911Frank B. Dehn & Co.,European Patent Attorneys, 179 Queen Victoria StreetLondon EC4V 4ELGBATBECHDEDKESFIFRGBGRIEITLILUMCNLPTSEJP960211519960726jaWO9700639519970220199709

The present invention relates to a heat exchanger comprising the features of the preamble of claim 1. Such a heat exchanger is known from DE-A-24 08 462.

There are also conventionally known heat exchangers including high-temperature fluid passages and low-temperature fluid passages defined in an annular space, which are described in Japanese Patent Application Laid-open Nos.57-2982, 57-2983 and 56-149585.

There is also a conventionally known heat exchanger described in Japanese Patent Publication No.58-40116, in which a folding plate blank composed of a plurality of first heat transfer plates and a plurality of second heat transfer plates alternately continuously formed to each other through first and second folding lines are folded into a zigzag fashion at the first and second folding lines, a gap between the adjacent first folding lines being closed by bonding of the first folding lines and a first end plate, a gap between the adjacent second folding lines being closed by bonding of the second folding line and a second end plate, and high-temperature fluid passages and low-temperature fluid passages are alternately formed between the adjacent first and second heat transfer plates.

The heat exchangers described in Japanese Patent Application Laid-open Nos.57-2982 and 57-2983 have a problem that the folding lines in the folding plate blank constituting the heat transfer plates are complicated and for this reason, a great deal of labor is required for a folding operation to increase a working cost. Another problem is that inlets of the high-temperature and low-temperature fluid passages open in a direction perpendicular to axes (i.e., radially) and hence, the flow of the fluid is abruptly bent at such open portions to produce a pressure loss. The heat exchangers described in Japanese Patent Application Laid-open No.56-149585 has a problem that the direction of flow paths at the inlets and outlets is perpendicular to the direction of flow paths in the high-temperature or low-temperature fluid passages and hence, the flow of the fluid is abruptly bent at such perpendicular portion to produce a pressure loss. Further, in this heat exchanger, ducts are connected to the inlets and outlets permitting the fluid to flow radially. Therefore, there is a problem that it is difficult to form the ducts along an axial direction of the heat exchanger, resulting in an increase in radial dimension of the heat exchanger.

The heat exchanger described in Japanese Patent Publication No.58-40116 has a problem that the sectional area of the flow path is constricted to about one half at the outlets and inlets of the high-temperature and low-temperature fluid passages, resulting in a great pressure loss produced at such portion. Moreover, the heat exchanger also has another problem that the outlets and inlets are formed by folding the folding plate blank and hence, the folding lines are complicated, resulting in a great deal of labor required for the folding operation to increase the manufacture cost. A further problem is that if the difference in pressure between the high-temperature or low-temperature fluid passages is large, a spacer is inserted between the first and second heat transfer plates to maintain the strength, resulting in increases in number of parts and in number of assembling steps by such a spacer. Further, the fluid outlet and inlet formed adjacent each other are intricate with each other and hence, if an attempt is made to partition the outlet and inlet by a partition member, the structure of the partition member becomes complicated, and the area of the bond area such as the brazed area is increased, resulting in a possibility of a fluid leakage produced.

The present invention has been accomplished with the above circumstances in view, and it is a first object of the present invention to provide a heat exchanger which has a simple structure, so that the heat exchanger is easy to manufacture and , wherein the pressure loss due to the bending of the flow path can be suppressed to the minimum.

It is a second object of the invention to provide a heat exchanger, wherein the pressure loss due to the bending of the flow path can be suppressed to minimum and moreover, the radial dimension can be decreased.

It is a third object of the invention to provide a heat exchanger, wherein the sectional area of the flow paths at the outlets and inlets of fluid passages can sufficiently be insured to suppress the pressure loss to the minimum and moreover, the outlets and inlets can be formed by a means other than the folding of the folding plate blank.

It is a fourth object of the invention to provide a heat exchanger, wherein the sectional area of the flow paths at the outlets and inlets of fluid passages can sufficiently be insured to suppress the pressure loss to the minimum and moreover, the accuracy and strength of the heat transfer plates can be maintained without increases in number of parts and number of assembling steps.

It is a fifth object of the invention to provide a heat exchanger, wherein the sectional area of the flow paths at the outlets and inlets of fluid passages can sufficiently be insured to suppress the pressure loss to the minimum and moreover, it is easy to partition the outlet and the inlet by a partition member.

In accordance with the invention these objects are solved in that the height of the projections is gradually increased outwards from the radially inner side, tip ends of the projections of the adjacent first and second heat transfer plates being brought into abutment against each other.

With such arrangement, it is possible not only to substantially reduce the number of the heat transfer plates of the heat exchanger to possibly decrease the bonding portions between the heat transfer plates, but also to easily and accurately maintain the axial symmetry of the heat exchanger. Moreover, flow paths of the high-temperature and low-temperature fluid passages do not bend abruptly at the inlets and the outlets and hence, it is possible to suppress the increase in flow path resistance to reduce the pressure loss.

Preferably, said high-temperature fluid passage inlets are formed by cutting axially opposite ends of said first and second heat transfer plates into an angle shape having two end edges, closing one of said two end edges at axially one ends of said high-temperature fluid passages, said high-temperature fluid passage outlets being formed by closing said one end edge at the axially other ends of said high-temperature fluid passages and opening the other end edge, said low-temperature fluid passage inlets being formed by closing said other edge at axially other ends of said low-temperature fluid passages and opening said one end edge, said low-temperature fluid passage outlets being formed by closing said other end edge at axially one ends of said low-temperature fluid passages.

With the above arrangement, a high-temperature fluid and a low-temperature fluid can be permitted to flow in opposite directions to provide an enhanced heat exchange efficiency. Flow paths of the high-temperature and low-temperature fluid passages are smoothly formed, but also sectional area of flow paths in the inlets and outlets can sufficiently be insured to suppress the generation of a pressure loss to the minimum. Further, the flow paths connected to the outsides of the inlets and the outlets can be easily formed to extend axially, thereby reducing the radial dimension of the heat exchanger, but also the inlets and outlets can be easily separated from each other to avoid the mixing of the high-temperature and low-temperature fluids.

Further, the need for folding the folding plate blank to form the inlets and the outlets can be eliminated to contribute to a reduction in manufacture cost.

Preferably said high-temperature fluid passage inlets are formed by cutting opposite ends of the first and second heat transfer plates in a flow path direction into an angle shape having two end edges, closing one of the two end edges at one ends of the high-temperature fluid passages in the flow path direction and opening the other end edge, said high-temperature fluid passage outlets are formed by closing the one end edge at the other ends of the high-temperature fluid passages and opening the other end edge, said low-temperature fluid passage inlets are formed by closing the other end edge at the other ends of the low-temperature fluid passages in the flow path direction and opening the one end edge, low-temperature fluid passage outlets formed by closing the other end edge at one ends of the low-temperature fluid passages and opening the one end edge, partition plates each bonded to an apex of the angle shape at the one end in the flow path direction to partition the high-temperature fluid passage inlets and the low-temperature fluid passage outlets from each other, and partition plates are each bonded to an apex of the angle shape at the other end in the flow path direction to partition the low-temperature fluid passage inlets and the high-temperature fluid passage outlets.

With the above arrangement, a high-temperature fluid and a low-temperature fluid can be permitted to flow in opposite directions to provide an enhanced heat exchange efficiency. Flow paths of the high-temperature and low-temperature fluid passages can be smoothly formed, and the sectional area of flow paths at the inlets and the outlets can sufficiently be insured to suppress the pressure loss to the minimum. Moreover, the inlets and the outlets can be easily separated from each other to avoid the mixing of the high-temperature and low-temperature fluids. Further, the reduction in sectional area of the flow paths at the inlets and the outlets due to the partition plates can be suppressed to the minimum and moreover, the area of bond portions between the first and second heat transfer plates and the partition plates can be suppressed to the minimum to diminish the possibility of a liquid leakage.

Preferred embodiments of the invention will now be described by way of example only, and with reference to the accompanying drawings in which:

A first embodiment of the present invention will now be described with reference to Figs.1 to 12.

As shown in Figs.1 and 2, a gas turbine engine E includes an engine body 1 in which a combustor, a compressor, turbine and the like are accommodated. An annular heat exchanger 2 is disposed to surround an outer periphery of the engine body 1. The heat exchanger 2 includes four modules 21, having a center angle of 90° and arranged circumferentially with side plates 3 sandwiched between the adjacent modules, and further includes combustion gas passages 4 through which a combustion gas of relatively high temperature passed through the turbine is passed, and air passages 5 through which air of relatively low temperature compressed in the compressor is passed. The passages 4 and 5 are formed circumferentially alternately (see Figs.5 to 9). A section in Fig.1 corresponds to the combustion gas passage 4 , and the air passages 5 are formed on this side and on the far side of the combustion gas passage 4.

The section shape of the heat exchanger 2 extending along an axis is of an axially longer and radially shorter flat hexagonal shape. A radially outer peripheral surface of the heat exchanger 2 is closed by a cylindrical outer casing 6 of a larger diameter, and a radially inner peripheral surface is closed by a cylindrical inner casing 7 of a smaller diameter. A front end side (a left side in Fig.1) in the section of the heat exchange 2 is cut into an angle shape, and an end plate 8 is brazed to an end face corresponding to an apex of the angle shape and connected to the outer periphery of the engine body 1. A rear end side (a right side in Fig.1) in the section of the heat exchange 2 is also cut in an angle shape, and an end plate 10 is brazed to an end face corresponding to the apex of the angle shape and connected to a rear outer housing 9.

Each of the combustion gas passages 4 in the heat exchanger 2 includes a combustion gas passage inlet 11 and a combustion gas passage outlet 12 at left and right upper locations in Fig.1. A downstream end of a combustion gas introducing duct 13 formed along the outer periphery of the engine body 1 is connected to the combustion gas passage inlet 11, and an upstream end of a combustion gas discharging duct 14 extending within the engine body 1 is connected to the combustion gas passage outlet 12.

Each of the air passages 5 in the heat exchange 2 includes an air passage inlet 15 and an air passage outlet 16 at right and left lower locations in Fig.1. A downstream end of an air introducing duct 17 formed along an inner periphery of the rear outer housing 9 is connected to the air passage inlet 15, and an air discharging duct 18 extending within the engine body 1 is connected to the air passage outlet 16.

In this manner, combustion gas and air flow in opposite directions and cross each other, as shown in Figs.3, 4 and 12, thereby realizing a so-called "cross-flow" having a high heat-exchange efficiency. That is, by permitting a higher-temperature fluid and a lower-temperature fluid to flow in opposite directions, a large difference in temperature between the higher-temperature fluid and the lower-temperature fluid can be maintained over the entire length of flow paths of the fluids to enhance the heat exchange efficiency.

The temperature of the combustion gas which has driven the turbine is about 600 to 700°C in the combustion gas passage inlets 11 , and the combustion gas is cooled down to about 300 to 400°C in the combustion gas passage outlets 12 by conducting a heat exchange between the combustion gas and the air when the combustion gas passes through the combustion gas passages 4. On the other hand, the temperature of the air compressed by the compressor is about 200 to 300°C in the air passage inlets 15 , and the air is cooled down to about 500 to 600°C in the air passage outlets 16 --- by conducting a heat exchange between the air and the combustion gas when the air passes through the air passages 5.

The structure of the heat exchanger 2 will be described below with reference to Figs.3 to 11.

As shown in Figs.3, 4 and 10, the modules 21 of the heat exchanger 2 is made from a folding plate blank 21 produced by cutting a thin metal plate such as a stainless steel or the like into a predetermined shape and then forming an irregularity on a surface of the cut plate by pressing. The folding plate blank 21 is constructed of first heat transfer plates S1 and second heat transfer plates disposed alternately, and is folded into a zigzag shape through crest folding lines L1 and valley folding lines L2. The term "crest folding" means that the blank is folded into a convex toward this side of a paper sheet surface, and the term "valley folding" means that the blank is folded into a convex toward the far side of the paper sheet surface. Each of the crest folding line L1 and the valley folding line L2 is not a simple straight line, but actually, is two substantially parallel lines for the purpose of forming a predetermined space between the first and second heat transfer plates S1 and S2 and moreover, opposite ends thereof are folded lines departing from a straight line for the purpose of forming closed projections 241 and 251 which will be described hereinafter.

A large number of first projections 22 and a large number of second projections 23 disposed in a grid manner are formed on each of the first and second heat transfer plates S1 and S2 by pressing. The first projections 22 protrude toward this side of the paper sheet surface of Fig.10, and the second projections 23 protrude toward the far side of the paper sheet surface of Fig.10. The first projections 22 and the second projections 23 are disposed alternately (i.e., so that the first projections 22 are not continuous to one another or the second projections 23 are not continuous to one another.

First projection stripes 24F and 24R protruding toward this side of the paper sheet surface of Fig.10 and second projection stripes 25F and 25R protruding toward the far side of the paper sheet surface of Fig.10 are formed at the front an rear ends, cut into the angle shape, of the first and second heat transfer plates S1 and S2 by pressing. For any of the first and second heat transfer plates S1 and S2, a pair of the front and rear first projection stripes 24F and 24R are disposed at diagonal locations, and a pair of the front and rear second projection stripes 25F and 25R are disposed at other diagonal locations.

As can be seen from Figs.3 and 10, when the first and second heat transfer plates S1 and S2 of the folding plate blank 21 are folded along the crest folding lines L1 to form the combustion gas passages 4 between both the first and second heat transfer plates S1 and S2, tip ends of the second projections 23 of the first heat transfer plate S1 and tip ends of the second projections 23 of the second heat transfer plate S2 are brought into abutment against each other and brazed to each other. In addition, the second projection stripes 25F and 25R of the first heat transfer plate S1 and the second projection stripes 25F and 25R of the second heat transfer plate S2 are brought into abutment against each other and brazed, thereby closing left and right lower portions of the combustion gas passage 4 shown in Fig.2, and the first projection stripes 24F and 24R of the first heat transfer plate S1 and the first projection stripes 24F and 24R of the second heat transfer plate S2 are opposed to each other and brazed, thereby defining the combustion gas passage inlet 11 and the combustion gas passage outlet 12 at the left and right upper portions of the combustion gas passage 4 shown in Fig.3, respectively. For the first heat transfer plate S1 shown in Fig.3, the back side thereof is shown based on the first heat transfer plate S1 shown in Fig.10.

As can be seen from Figs4 and 10, when the first heat transfer plates S1 and the second heat transfer plates S2 of the folding plate blank 21 are folded along the valley folding lines L2 to define the air passages 5 between both first and second heat transfer plates S1 and S2 , the tip ends of the first projections 22 of the first heat transfer plate S1 and the tip ends of the first projections 22 of the second heat transfer plate S2 are brought into abutment against each other and brazed to each other. In addition, the first projection stripes 24F and 24R of the first heat transfer plate S1 and the first projection stripes 24F and 24R of the second heat transfer plate S2 are brought into abutment against each other and brazed to each other, thereby closing left and right lower portions of the air passage 5 shown in Fig.4, and the second projection stripes 25F and 25R of the first heat transfer plate S1 and the second projection stripes 25F and 25R of the second heat transfer plate S2 are opposed to each other to define the air passage inlet 15 and the air passage outlet 16 at the right and left lower portions of the air passage 5 shown in Fig.4, respectively. For the second heat transfer plate S2 shown in Fig.4, the surface side thereof is shown based on the second heat transfer plate S2 shown in Fig.10.

A state in which the air passages 5 have been closed by the first projection stripes 24F is shown in an upper portion (a radially outer side) of Fig.9, and a state in which the combustion gas passages 4 have been closed by the second projection stripes 25F is shown in a lower portion (a radially outer side) of Fig.9.

The first and second projections 22 and 23 each have a substantially truncated conical shape, and their tip end portions are brought into surface contact with each other in order to enhance the brazing strength which will be described hereinafter. The first and second projection stripes 24F , 24R 25F and 25R each also have a substantially truncated conical section, and their tip end portions are also brought into surface contact with each other in order to enhance the brazing strength.

As can be seen from Figs.3, 4 and 11, when the folding plate blank 21 is folded ma zigzag fashion, closing projections 241 and 251 are formed at axially inner ends (portions connected to the crest folding lines L1 and the valley folding lines L2) of the first and second projection stripes 24F , 24R 25F and 25R to extend integrally from the first and second projection stripes 24F , 24R 25F and 25R. When the tip ends of the opposed first projection stripes 24F and 24R have been bonded to each other, the tip ends of the closing projections 241 connected to the first projection stripes 24F and 24R are also bonded to each other. When the tip ends of the opposed second projection stripes 25F have been bonded to each other, the tip ends of the closing projections 251 connected to the second projection stripes 25F are also bonded to each other. The radially inner surface of the outer casing 6 and the radially outer peripheral surface of the inner casing 7 are connected to the radially outer and inner peripheral surfaces of the bonded closing projections 241 and 251 , respectively.

A state in which the air passages 5 has been closed by the closing projections 241 is shown in an upper portion (a radially outer portion) of Fig.7 and in Fig.8. A state in which the combustion gas passages 4 have been closed by the closing projections 251 is shown in a lower portion (a radially inner portion) of Fig.7. The closing of the air passages 5 by the closing projections 241 is also shown in a portion A of Fig.4, and the closing of the combustion gas passages 4 by the closing projections 251 is also shown in a portion A of Fig.3.

As can be seen from Figs.5 and 6, radially inner peripheral portions of the air passages 5 are automatically closed because they correspond to folded portions (the valley folding lines L2) of the folding plate blank 21, but radially outer portions of the air passages 5 are open, and such open portions are closed by the outer casing 6. On the other hand, radially outer peripheral portions of the combustion gas passages 4 are automatically closed because they correspond to folded portions (the crest folding lines L1) of the folding plate blank 21, but radially inner peripheral portions of the combustion gas passages 4 are open, and such open portions are closed by the inner casing 7.

In this way, the heat exchange efficiency is enhanced by disposing the combustion gas passages 4 and the air passages 5 alternately in the circumferential direction in a possibly wide area extending along the radially outer and inner peripheral portions of the heat exchanger 2 (see Fig.5).

When the modules 21 of the heat exchanger 2 are fabricated by folding the folding plate blank 21 in the zigzag fashion, the first and second heat transfer plates S1 and S2 are disposed radiately from the center of the heat exchanger 2. Therefore, the distance between the adjacent first and second heat transfer plates S1 and S2 is a maximum at the radially outer peripheral portion contacting with the outer casing 6 and a minimum at the radially inner peripheral portion contacting with the inner casing 7. Therefore, the height of the first projections 22 , the second projections 23 , the first projection stripes 24F, 24R and the second projection stripes 25F, 25R is gradually increased from the radially inner side toward the radially outer side. Thus, the first and second heat transfer plates S1 and S2 can be disposed exactly radiately (see Figs.5 and 7).

By employing the above-described structure of the radiately folding plate, the outer and inner casings 6 and 7 can be concentrically located, and the axial symmetry of the heat exchanger 2 can be accurately maintained.

By constituting the heat exchanger 2 by a combination of the four modules 21 of the same structure, it is possible to facilitate the manufacture of the heat exchanger 2 and to simplify the structure of the heat exchanger 2. By folding the folding plate blank 21 radiately and in the zigzag fashion to forming the first and second heat transfer plates S1 and S2 in a continuous manner, the number of parts and the number of brazing points can be substantially reduced, but also the dimensional accuracy of the finished article can be enhanced, as compared with a large number of first heat transfer plates S1 independent from one another and a large number of second heat transfer plates S2 independent from one another are alternately brazed.

During operation of the gas turbine engine E, the pressure in the combustion gas passages 4 is relatively low, and the pressure in the air passages 5 is relatively high. Therefore, a flexural load is applied to the first and second heat transfer plates S1 and S2 by a difference between these pressures, but a sufficient rigidity capable of withstanding such load can be provided by the first and second projections 22 and 23 brought into abutment against each other and brazed to each other.

The surface areas of the first and second heat transfer plates S1 and S2 (i.e., the surface areas of the combustion gas passages 4 and the air passages 5 ) are increased by the first and second projections 22 and 23 , and moreover, the flows of the combustion gas and the air are agitated, thereby enabling an enhancement in heat exchange efficiency.

Further, the front and rear ends of the heat exchanger 2 are cut into the angle shape, and the combustion gas passage inlet 11 and the air passage outlet 16 are defined along two sides of the angle shape at the front end of the heat exchanger 2, while the combustion gas passage outlet 12 and the air passage inlet 15 are defined along two sides of the angle shape at the rear end of the heat exchanger 2. Therefore, large sectional areas of flow paths in the inlets 11 and 15 the outlets 12 and 16 can be insured to suppress the pressure loss to the minimum, as compared with the case where inlets 11 and 15 and outlets 12 and 16 are defined without cutting of the front and rear ends of the heat exchanger 2 into an angle shape.

Moreover, since the inlets 11 and 15 and the outlets 12 and 16 are defined along the two sides of the angle shape, the flow paths of the combustion gas and the air flowing into and out of the combustion gas passages 4 and the air passages 5 can be smoothed to further reduce the pressure loss, but also the ducts connected to the inlets 11 and 15 and the outlets 12 and 16 can be disposed to extend axially without being abruptly bent, thereby reducing the radial dimension of the heat exchanger 2.

Further, since the end plates 8 and 10 are brazed to the end faces at the tips of the front and rear ends of the heat exchanger 2 formed into the angle shape, the brazing area cab be minimized to decrease the possibility of leakage of the combustion gas and the air due to a brazing failure. Moreover, it is possible to simply and reliably partition the inlets 11 and 15 and the outlets 12 and 16 while suppressing the decrease in opening areas of the inlets 11 and 15 and the outlets 12 and 16.

Fig. 13 shows a second embodiment of the present invention. In the second embodiment, either inlets 11 and outlets 12 of combustion gas passages 4 are defined at a radially outer side, and outlets 16 and inlets 15 of air passages 5 are defined radially inside of the inlets 11 and outlets 12. Thus, the combustion gas and the air flowing in the opposite directions intersect each other in the first embodiment, but the combustion gas and the air flowing in the opposite directions flow by each other in the second embodiment.

The other structures in the second embodiment are the same as in the first embodiment, and functions and effects similar to those in the first embodiment can be provided.

Although the embodiments of the present invention have been described in detail, it will be understood that the present invention is not limited to the above-described embodiments and various modifications in design may be made without departing from the scope of the invention defined in claims.

For example, the heat exchanger 2 for the gas turbine engine E has been illustrated in the embodiments, but the present invention is also applicable to a heat exchanger for use in another device and apparatus. In the features of claims 7 and 8, the first and second heat transfer plates S1 and S2 are unnecessarily not formed in the folded structure, and first and second independent heat transfer plates S1 and S2 may be combined with each other.

 A heat exchanger (2) comprising axially extending high-temperature and low-temperature fluid passages (4,5) formed circumferentially alternately in an annular space defined between a radially outer peripheral wall (6) and a radially inner peripheral wall (7), wherein by folding a folding plate blank (21) comprised of a plurality of first heat transfer plates (S1) and a plurality of second heat transfer plates (S2) connected alternately through folding lines (L1,L2), in a zigzag fashion, so that the first and second heat transfer plates (S1,S2) are disposed radiately between the radially outer and inner peripheral walls (6,7), said high-temperature and low-temperature fluid passages (4,5) are formed circumferentially alternately between the adjacent first and second heat transfer plates (S1,S2), and high-temperature fluid passage inlets (11) and low-temperature fluid passage outlets (12) are formed to open into axially opposite ends of said high-temperature fluid passages (4), and low-temperature fluid passage inlets (15) and low-temperature fluid passage outlets (16) are formed to open into axially opposite ends of said low-temperature fluid passages (5), and wherein a large number of projections (22,23) are formed on opposite surfaces of said first and second heat transfer plates, characterised in that the height of the projections (22,23) is gradually increased outwards from the radially inner side, tip ends of the projections of the adjacent first and second heat transfer plates (S1,S2) being brought into abutment against each other. A heat exchanger as claimed in claim 1, wherein the tip ends of the projections (22,23) abutting against each other are bonded to each other. A heat exchanger as claimed in claim 1 or 2, wherein said high-temperature fluid passage inlets (11) are formed by cutting axially opposite ends of said first and second heat transfer plates (S1,S2) into an angle shape having two end edges, closing one of said two end edges at axially one ends of said high-temperature fluid passages (4), said high-temperature fluid passage outlets (12) being formed by closing said one end edge at the axially other ends of said high-temperature fluid passages (4) and opening the other end edge, said low-temperature fluid passage inlets (15) being formed by closing said other edge at axially other ends of said low-temperature fluid passages (5) and opening said one end edge, said low-temperature fluid passage outlets (16) being formed by closing said other end edge at axially one ends of said low-temperature fluid passages (5). A heat exchanger as claimed in claim 3, further including projection stripes (24F, 24R 25F,25R) formed on the adjacent first and second heat transfer plates to extend along said end edges, said end edges being closed by tip ends of said projection stripes being brought into abutment against each other. A heat exchanger as claimed in claim 4, wherein the height of each of said projection stripes (24F,24R,25F,25R) is gradually increased outwards from the radially inner side, and the tip ends of the projection stripes abutting against each other are bonded to each other. A heat exchanger as claimed in any preceding claim, wherein said heat exchanger is formed by a plurality of partially annular heat exchanger modules (21) circumferentially coupled to one another. A heat exchanger as claimed in claim 1, wherein said high-temperature fluid passage inlets (11) are formed by cutting opposite ends of said first and second heat transfer plates (S1,S2) in a flow path direction into an angle shape having two end edges, closing one of said two end edges at one ends of said high-temperature fluid passages (4) in the flow path direction and opening the other end edge, said high-temperature fluid passage outlets (12) are formed by closing said one end edge at the other ends of said high-temperature fluid passages (4) and opening said other end edge, said low-temperature fluid passage inlets (15) are formed by closing said other end edge at the other ends of said low-temperature fluid passages (5) in the flow path direction and opening said one end edge, said low-temperature fluid passage outlets (16) are formed by closing the other end edge at one ends of said low-temperature fluid passages (5) and opening said one end edge, wherein partition plates (8) are each bonded to an apex of said angle shape at the one end in the flow path direction to partition said high-temperature fluid passage inlets (11) and said low-temperature fluid passage outlets (16) from each other, and partition plates (10) are each bonded to an apex of said angle shape at the other end in the flow path direction to partition said low-temperature fluid passage inlets (15) and said high-temperature fluid passage outlets (12). Wärmetauscher (2), umfassend axial sich erstreckende Hochtemperatur- und Niedrigtemperaturfluidpassagen (4, 5), die in Umfangsrichtung abwechselnd in einem ringförmigen Raum ausgebildet sind, der zwischen einer radial äußeren Umfangswand (6) und einer radial inneren Umfangswand (7) begrenzt ist, wobei durch Falzen eines Falzplattenrohlings (21), der gebildet ist von einer Mehrzahl von ersten Wärmetransferplatten (S1) und einer Mehrzahl von zweiten Wärmetransferplatten (S2), die abwechselnd durch Falzlinien (L1, L2) verbunden sind, in einer Zickzack-Weise, so dass die ersten und zweiten Wärmetransferplatten (S1, S2) radial zwischen den radial äußeren und inneren Umfangswänden (6, 7) angeordnet werden, die Hochtemperatur- und Niedrigtemperaturfluidpassagen (4, 5) in Umfangsrichtung abwechselnd ausgebildet werden zwischen den benachbarten ersten und zweiten Wärmetransferplatten (S1, S2), wobei Hochtemperaturfluidpassageneinlässe (11) und Niedrigtemperaturfluidpassagenauslässe (12) ausgebildet sind, um sich in axial entgegengesetzte Enden der Hochtemperaturfluidpassagen (4) zu öffnen, und wobei Niedrigtemperaturfluidpassageneinlässe (15) und Niedrigtemperaturfluidpassagenauslässe (16) ausgebildet sind, um sich in axial entgegengesetzte Enden der Niedrigtemperaturfluidpassagen (5) zu öffnen, und wobei eine große Anzahl von Vorsprüngen (22, 23) an gegenüberliegenden Oberflächen der ersten und zweiten Wärmetransferplatten ausgebildet sind, dadurch gekennzeichnet, dass die Höhe der Vorsprünge (22, 23) von der radial inneren Seite nach außen hin graduell ansteigend vorgesehen ist, wobei Spitzenenden der Vorsprünge der benachbarten ersten und zweiten Wärmetransferplatten (S1, S2) zur Anlage gegeneinander gebracht sind. Wärmetauscher nach Anspruch 1, wobei die gegeneinander anliegenden Spitzenenden der Vorsprünge (22, 23) miteinander verbunden sind. Wärmetauscher nach Anspruch 1 oder 2, wobei die Hochtemperaturfluidpassageneinlässe (11) ausgebildet sind durch Schneiden von axial entgegengesetzten Enden der ersten und zweiten Wärmetransferplatten (S1, S2) zu einer winkligen Gestalt mit zwei Endrändern, Schließen eines der zwei Endränder an den axial einen Enden der Hochtemperaturfluidpassagen (4), wobei die Hochtemperaturfluidpassagenauslässe (12) gebildet sind durch Schließen des einen Endrands an den axial anderen Enden der Hochtemperaturfluidpassagen (4), und Öffnen des andere Endrands, wobei die Niedrigtemperaturfluidpassageneinlässe (15) ausgebildet sind durch Schließen des anderen Rands an axial anderen Enden der Niedrigtemperaturfluidpassagen (5) und Öffnen des einen Endrands, wobei die Niedrigtemperaturfluidpassagenauslässe (16) ausgebildet sind durch Schließen des anderen Endrands axial an Enden der Niedrigtemperaturfluidpassagen (5). Wärmetauscher nach Anspruch 3, ferner umfassend Vorsprungstreifen (24F, 24R, 25F, 25R), die an den benachbarten ersten und zweiten Wärmetransferplatten ausgebildet sind, um sich längs der Endränder zu erstrecken, wobei die Endränder geschlossen sind durch Spitzenenden der Vorsprungstreifen, die gegeneinander zur Anlage gebracht sind. Wärmetauscher nach Anspruch 4, wobei die Höhe jedes der Vorsprungstreifen (24F, 24R, 25F, 25R) von der radial inneren Seite nach außen hin graduell ansteigend vorgesehen ist und die Spitzenenden der gegeneinander zur Anlage gebrachten Vorsprungstreifen miteinander verbunden sind. Wärmetauscher nach einem vorangehenden Anspruch, wobei der Wärmetauscher gebildet ist durch eine Mehrzahl von teilringartigen Wärmetauschermodulen (21), die in Umfangsrichtung aneinander gekoppelt sind. Wärmetauscher nach Anspruch 1, wobei die Hochtemperaturfluidpassageneinlässe (11) ausgebildet sind durch Schneiden von gegenüberliegenden Enden der ersten und zweiten Wärmetransferplatten (S1, S2) in einer Flusspfadrichtung zu einer winkligen Gestalt mit zwei Endrändern, Schließen eines der zwei Endränder an Enden der Hochtemperaturfluidpassagen (4) in der Flusspfadrichtung und Öffnen des anderen Endrands, wobei die Hochtemperaturfluidpassagenauslässe (12) gebildet sind durch Schließen des einen Endrands an den anderen Enden der Hochtemperaturfluidpassager (4) und Öffnen des anderen Endrands, wobei die Niedrigtemperaturfluidpassageneinlässe (15) ausgebildet sind durch Schließen des anderen Endrands an den anderen Enden der Niedrigtemperaturfluidpassagen (5) in der Flusspfadrichtung und Öffnen des einen Endrands, wobei die Niedrigtemperaturfluidpassagenauslässe (16) gebildet sind durch Schließen des anderen Endrands an den Enden der Niedrigtemperaturfluidpassagen (5) und Öffnen des einen Endrands, wobei Aufteilungsplatten (8) jeweils mit einer Spitze der winkligen Gestalt an dem einen Ende in der Flusspfadrichtung verbunden sind, um die Hochtemperaturfluidpassageneinlässe (11) und die Niedrigtemperaturfluidpassagenauslässe (16) voneinander zu trennen, und wobei Aufteilungsplatten (10) jeweils verbunden sind mit einer Spitze der winkligen Gestalt an dem anderen Ende in der Flusspfadrichtung, um die Niedrigtemperaturfluidpassageneinlässe (15) und die Hochtemperaturfluidpassagenauslässe (12) voneinander zu trennen. Echangeur de chaleur (2) comprenant des passages de fluide à haute température et à basse température s'étendant de façon axiale (4, 5) formés de façon circonférentielle en alternance dans un espace annulaire défini entre une paroi radiale périphérique extérieure (6) et une paroi radiale périphérique intérieure (7), dans lequel, en plissant une ébauche de plaque à plier (21) composée d'une pluralité de premières plaques de transfert de chaleur (S1) et d'une pluralité de secondes plaques de transfert de chaleur (S2) reliées en alternance par des lignes de pliage (L1, L2), en zigzag, de sorte que les premières et secondes plaques de transfert de chaleur (S1, S2) sont disposées de façon rayonnante entre les parois radiales périphériques extérieure et intérieure (6, 7), lesdits passages de fluide à haute température et à basse température (4, 5) sont formés de façon circonférentielle en alternance entre les premières et secondes plaques de transfert de chaleur adjacentes (S1, S2), et des entrées de passage de fluide à haute température (11) et des sorties de passage de fluide à basse température (12) sont formées pour déboucher dans les extrémités opposées de façon axiale desdits passages de fluide à haute température (4), et des entrées de passage de fluide à basse température (15) et des sorties de passage de fluide à basse température (16) sont formées pour déboucher dans les extrémités opposées de façon axiale desdits passages de fluide à basse température (5), et dans lequel un grand nombre de parties en saillie (22, 23) sont formés sur les surfaces opposées desdites premières et secondes plaques de transfert de chaleur, caractérisé en ce que la hauteur des parties en saillie (22, 23) est progressivement augmentée vers l'extérieur en partant du côté radial intérieur, les extrémités de tête des parties en saillie des premières et secondes plaques de transfert de chaleur adjacentes (S1, S2) étant amenées en butée les unes contre les autres. Echangeur de chaleur selon la revendication 1, dans lequel les extrémités de tête des parties en saillie (22, 23) butant les unes contre les autres sont liées les unes aux autres. Echangeur de chaleur selon la revendication 1 ou 2, dans lequel lesdites entrées de passage de fluide à haute température (11) sont formées en coupant de façon axiale les extrémités opposées desdites premières et secondes plaques de transfert (S1, S2) en forme d'angle ayant deux bords d'extrémité, fermant l'un desdits deux bords d'extrémité au niveau d'extrémités axiales particulières desdits passages de fluide à haute température (4), lesdites sorties de passage de fluide à haute température (12) étant formées en fermant ledit bord d'extrémité particulier au niveau des autres extrémités axiales desdits passages de fluide à haute température (4) et ouvrant l'autre bord d'extrémité, lesdites entrées de passage de fluide à basse température (15) étant formées en fermant ledit autre bord au niveau des autres extrémités axiales desdits passages de fluide à basse température (5) et ouvrant ledit bord d'extrémité particulier, lesdites sorties de passage de fluide à basse température (16) étant formées en fermant ledit autre bord d'extrémité au niveau des extrémités axiales particulières desdits passages de fluide à basse température (5). Echangeur de chaleur selon la revendication 3, comprenant de plus des bandes en saillie (24F, 24R, 25F, 25R) formées sur les premières et secondes plaques de transfert de chaleur adjacentes pour s'étendre le long desdits bords d'extrémité, lesdits bords d'extrémité étant fermés par les extrémités de tête desdites bandes en saillie amenées en butée les unes contre les autres. Echangeur de chaleur selon la revendication 4, dans lequel la hauteur de chacune desdites bandes en saillie (24F, 24R, 25F, 25R) est progressivement augmentée vers l'extérieur en partant du côté radial intérieur, et les extrémités de tête des bandes en saillie amenées en butée les unes contre les autres sont liées les unes aux autres. Echangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel ledit échangeur de chaleur est formé par une pluralité de modules d'échangeur de chaleur partiellement annulaires (21) accouplés les uns aux autres de façon circonférentielle. Echangeur de chaleur selon la revendication 1, dans lequel lesdites entrées de passage de fluide à haute température (11) sont formées en coupant les extrémités opposées desdites premières et secondes plaques de transfert de chaleur (S1, S2) dans un sens de flux d'écoulement en forme d'angle ayant deux bords d'extrémité, fermant l'un desdits deux bords d'extrémité au niveau des extrémités particulières desdits passages de fluide à haute température (4) dans le sens de flux d'écoulement et ouvrant l'autre bord d'extrémité, lesdites sorties de passage de fluide à haute température (12) sont formées en fermant ledit bord d'extrémité particulier au niveau des autres extrémités desdits passages de fluide à haute température (4) et ouvrant ledit autre bord d'extrémité, lesdites entrées de passage de fluide à basse température (15) sont formées en fermant ledit autre bord d'extrémité au niveau des autres extrémités desdits passages de fluide à basse température (5) dans le sens de flux d'écoulement et ouvrant ledit bord d'extrémité particulier, lesdites sorties de passage de fluide à basse température (16) sont formées en fermant l'autre bord d'extrémité au niveau des extrémités particulières desdits passages de fluide à basse température (5) et ouvrant ledit bord d'extrémité particulier, dans lequel des plaques de séparation (8) sont liées chacune à un sommet de ladite forme d'angle au niveau de l'extrémité particulière dans le sens de flux d'écoulement, pour séparer lesdites entrées de passage de fluide à haute température (11) et lesdites sorties de passage de fluide à basse température (16) les unes des autres, et des plaques de séparation (10) sont liées chacune à un sommet de ladite forme d'angle au niveau de l'autre extrémité dans le sens de flux d'écoulement pour séparer lesdites entrées de passage de fluide à basse température (15) et lesdites sorties de passage de fluide à haute température (12).